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CN1069742C - centrifugal compressor - Google Patents

centrifugal compressor Download PDF

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Publication number
CN1069742C
CN1069742C CN95102414A CN95102414A CN1069742C CN 1069742 C CN1069742 C CN 1069742C CN 95102414 A CN95102414 A CN 95102414A CN 95102414 A CN95102414 A CN 95102414A CN 1069742 C CN1069742 C CN 1069742C
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Prior art keywords
blade
impeller
side wall
stator blade
diffuser
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CN95102414A
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CN1116280A (en
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寺崎政敏
中川幸二
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Hitachi Ltd
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Hitachi Ltd
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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D29/00—Details, component parts, or accessories
    • F04D29/40—Casings; Connections of working fluid
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D29/00—Details, component parts, or accessories
    • F04D29/40—Casings; Connections of working fluid
    • F04D29/42—Casings; Connections of working fluid for radial or helico-centrifugal pumps
    • F04D29/44—Fluid-guiding means, e.g. diffusers
    • F04D29/441—Fluid-guiding means, e.g. diffusers especially adapted for elastic fluid pumps
    • F04D29/444—Bladed diffusers
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F05—INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
    • F05D—INDEXING SCHEME FOR ASPECTS RELATING TO NON-POSITIVE-DISPLACEMENT MACHINES OR ENGINES, GAS-TURBINES OR JET-PROPULSION PLANTS
    • F05D2240/00—Components
    • F05D2240/10—Stators
    • F05D2240/12—Fluid guiding means, e.g. vanes
    • F05D2240/121—Fluid guiding means, e.g. vanes related to the leading edge of a stator vane
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F05—INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
    • F05D—INDEXING SCHEME FOR ASPECTS RELATING TO NON-POSITIVE-DISPLACEMENT MACHINES OR ENGINES, GAS-TURBINES OR JET-PROPULSION PLANTS
    • F05D2250/00—Geometry
    • F05D2250/50—Inlet or outlet
    • F05D2250/52—Outlet

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Structures Of Non-Positive Displacement Pumps (AREA)

Abstract

A centrifugal compressor has a diffuser operative to convert the kinetic energy of fluid discharged from an impeller into pressure and having a shroud, a main shroud, and stationary vanes disposed in the diffuser. The distance between the shroud and the main shroud is smaller at an inlet side of the diffuser than at an outlet side thereof. The stationary vanes are integral with the one of the shroud and the main shroud that is perpendicular to the axis of rotation of the impeller so that an end surface of each of the stationary vanes forms a free end.

Description

离心式压缩机centrifugal compressor

本发明涉及离心式压缩机，特别是涉及一种具有特别宽的运行范围的高效率的离心式压缩机。The present invention relates to centrifugal compressors, and more particularly to a high-efficiency centrifugal compressor with a particularly wide operating range.

目前，在具有固定叶片的扩压器中，固定叶片在流道出口侧的截面与其在流道进口侧的截面之比值设定为大于1(即出口侧截面大于进口侧截面)，以减少通过固定叶片的流体的流量。另一方面，为了减小压缩机的整体尺寸，希望最大限度地减小压缩机的扩压器的外径。已经知道，相对于固定叶片进口侧的宽度来增大固定叶片出口侧的宽度，可以有效地减小扩压器的外径(例如，如日本未审查专利公开No.58-183899所公开的)。At present, in the diffuser with fixed vanes, the ratio of the section of the fixed vane on the outlet side of the flow channel to the section on the inlet side of the flow channel is set to be greater than 1 (that is, the section on the outlet side is larger than the section on the inlet side) to reduce the passage of The flow rate of the fluid that holds the vanes. On the other hand, in order to reduce the overall size of the compressor, it is desirable to minimize the outer diameter of the diffuser of the compressor. It is known that increasing the width of the outlet side of the fixed vane relative to the width of the inlet side of the fixed vane can effectively reduce the outer diameter of the diffuser (for example, as disclosed in Japanese Unexamined Patent Publication No. 58-183899) .

在具有叶片扩压器的离心式压缩机中，运转范围是由扩压器限定的，它由于在高流量侧出现阻塞和扩压器在低流量侧出现流体分离而加以限定。固定叶片间的流道的截面主要会影响阻塞的发生，而固定叶片间的流道的截面和叶片角度将会影响分离。对于防止出现分离，已经有一些方案，其一是使固定叶片的前边从侧壁向主侧壁倾斜，其二是在固定叶片的前缘附近设置辅助叶片(例如见日本未审查专利公开No.1-247798)。In centrifugal compressors with vane diffusers, the operating range is defined by the diffuser due to clogging on the high flow side and fluid separation of the diffuser on the low flow side. The cross-section of the flow channel between the fixed vanes will mainly affect the occurrence of clogging, while the cross-section of the flow channel between the fixed vanes and the vane angle will affect the separation. For preventing separation, there have been some proposals, one is to make the front edge of the fixed vane inclined from the side wall to the main side wall, and the other is to provide auxiliary vanes near the front edge of the fixed vane (for example, see Japanese Unexamined Patent Publication No. 1-247798).

在日本未审查专利公开No.58-183899所公开的结构中，固定叶片间的间隙是变化的，使进口侧的间隙大于出口侧的间隙，因此，位于出口侧的叶片角度比位于进口侧的叶片角度更接近于径向，而使出口侧的气流流动更趋近于径向，其结果是，在低流量侧的损失加大(当蜗壳在扩压器下游侧成形时，此损失特别大)。由于固定叶片的成形或支承面是弯曲的，所以工作级的数量增加了。In the structure disclosed in Japanese Unexamined Patent Publication No. 58-183899, the clearance between the fixed blades is changed so that the clearance on the inlet side is larger than the clearance on the outlet side, so that the angle of the blade on the outlet side is greater than that on the inlet side. The vane angle is closer to the radial direction, so that the air flow on the outlet side is closer to the radial direction. As a result, the loss on the low flow side is increased (this loss is especially important when the volute is formed on the downstream side of the diffuser. big). Due to the curved profile or bearing surface of the stationary vane, the number of working stages is increased.

在日本未审查专利公开No.1-247798公开的结构中，可以利用固定叶片或辅助叶片的前缘形状的效应来抑制低流量侧的气流分离，但扩压器下游侧的损失变大。In the structure disclosed in Japanese Unexamined Patent Publication No. 1-247798, the effect of the leading edge shape of the fixed vane or the auxiliary vane can be used to suppress the air flow separation on the low flow side, but the loss on the downstream side of the diffuser becomes large.

本发明的目的是提供这样一种离心式压缩机，它容易制造并具有宽的运转范围和高的效率。The object of the present invention is to provide a centrifugal compressor which is easy to manufacture and has a wide operating range and high efficiency.

为实现这一目的，根据本发明的一个方面，提供了一种离心式压缩机，它包括：一个叶轮；一个用于将叶轮排出的流体的动能转换为压力的扩压器，该扩压器具有一个侧壁和一个主侧壁，侧壁与主侧壁之一与叶轮的转动轴线相垂直；以及设置在扩压器中的固定叶片，其中，所述侧壁和主侧壁间在所述扩压器的进口侧的距离小于在所述扩压器的出口侧的距离，所述固定叶片与所述侧壁和主侧壁中的那个与所述叶轮的转动轴线相垂直的臂成为一体，使得每个所述固定叶片在其一端沿其高度方向的端面构成一自由端，所述每个固定叶片在所述进口侧的高度小于在所述出口侧的高度。To achieve this purpose, according to one aspect of the present invention, a centrifugal compressor is provided, comprising: an impeller; a diffuser for converting the kinetic energy of the fluid discharged from the impeller into pressure, the diffuser having a side wall and a main side wall, one of the side wall and the main side wall being perpendicular to the axis of rotation of the impeller; and stationary vanes disposed in the diffuser, wherein the The distance on the inlet side of the diffuser is smaller than the distance on the outlet side of the diffuser, the fixed vane and the arm of the side wall and the main side wall perpendicular to the axis of rotation of the impeller become Integral, so that the end surface of each of the fixed blades along the height direction at one end forms a free end, and the height of each of the fixed blades on the inlet side is smaller than that on the outlet side.

由于每个固定叶片与侧壁或主侧壁中的那个垂直于叶轮转动轴线的壁的平面整体成形，且具有一个自由端，所以用于制造固定叶片和支承固定叶片的侧壁或主侧壁的坯料易于加工，因为上述表面是平的。Since each stationary vane is integrally formed with the plane of the sidewall or main sidewall which is perpendicular to the axis of rotation of the impeller and has a free end, it is used to manufacture the stationary vane and to support the sidewall or main sidewall of the stationary vane The blanks are easy to machine because the above surface is flat.

根据本发明的另一方面，靠近出口侧的每个固定叶片与叶轮的径向所成的角度大于靠近进口侧的该固定叶片与叶轮的径向所成的角度，这样就降低了低流量侧的气流阻塞，从而扩大了运行范围。According to another aspect of the present invention, the angle formed by each fixed vane near the outlet side with the radial direction of the impeller is larger than the angle formed between the fixed vane near the inlet side and the radial direction of the impeller, thus reducing the flow rate on the low flow side. The air flow is blocked, thereby expanding the operating range.

根据本发明的又一方面，每个固定叶片上靠近侧壁的一个前缘部分比其上靠近主侧壁的另一前缘部分更接近于叶轮，或者辅助叶片与所述侧壁和主侧壁中的那个与所述叶轮的转动轴线相垂直的壁整体成形，每个所述辅助叶片的弦长小于每个所述固定叶片的弦长，而其高度等于或小于每个所述固定叶片的高度，辅助叶片设置在靠近所述固定叶片的所述进口端，使每个所述辅助叶片的两个表面中的一个表面对着一个相关的固定叶片。因此，固定叶片或辅助叶片的前缘强制引导来自叶轮的液体，从而抑制在叶轮的出口侧和固定叶片的前缘之间出现逆流。在扩压器中的低流量侧的气流塞也由此降低，这样就扩大了运转范围。According to a further aspect of the invention, a leading edge portion of each stationary blade near the side wall is closer to the impeller than the other leading edge portion of the stationary blade near the main side wall, or the auxiliary blade is connected to said side wall and the main side wall. The one of the walls perpendicular to the rotation axis of the impeller is integrally formed, each of the auxiliary blades has a chord length smaller than that of each of the fixed blades, and a height equal to or less than that of each of the fixed blades The height of the auxiliary vane is arranged close to the inlet end of the fixed vane so that one of the two surfaces of each of the auxiliary vanes faces an associated fixed vane. Therefore, the leading edge of the stationary vane or the auxiliary vane forcibly guides the liquid from the impeller, thereby suppressing the occurrence of reverse flow between the outlet side of the impeller and the leading edge of the stationary vane. The flow plug on the low-flow side of the diffuser is thereby lowered, which extends the operating range.

根据本发明的再一方面，一块隔板连到每个辅助叶片的一个下游端，且沿着一个相关的固定叶片延伸，隔板的高度小于辅助叶片的高度，以抑制来自辅助叶片根部的涡流。由于减小这种涡流所消耗的流体能量，从而提高离心式压缩机的效率。According to still another aspect of the present invention, a bulkhead is connected to a downstream end of each auxiliary vane and extends along an associated fixed vane, the height of the bulkhead being less than the height of the auxiliary vanes to suppress vortices from the roots of the auxiliary vanes . The efficiency of the centrifugal compressor is increased by reducing the fluid energy consumed by this vortex.

另外，由于扩压器在进口侧的宽度相对于其出口侧的宽度减小了，所以每个固定叶片在进口侧的宽度也相对其出口侧宽度减小了。这样就降低了流体在出口侧的径向速度，从而降低了径向速度的能量损失。In addition, since the width of the diffuser on the inlet side is reduced relative to the width on the outlet side thereof, each stationary vane is also reduced in width on the inlet side relative to its outlet side width. This reduces the radial velocity of the fluid on the outlet side, thereby reducing the energy loss in the radial velocity.

通过下面结合附图对本发明的优选实施例的详细说明，可以更清楚地理解本发明的上述及其它目的、特征和优点。The above and other objects, features and advantages of the present invention can be more clearly understood through the following detailed description of preferred embodiments of the present invention in conjunction with the accompanying drawings.

图1是本发明的离心式压缩机的一个实施例的横截面图，它是沿着包含叶轮的转动轴线的平面截取的。1 is a cross-sectional view of one embodiment of the centrifugal compressor of the present invention, taken along a plane containing the axis of rotation of the impeller.

图2是图1所示实施例中的固定叶片的平面图，表示了叶片的设置情况。Fig. 2 is a plan view of the stationary vanes in the embodiment shown in Fig. 1, showing the arrangement of the vanes.

图3是本发明的第二实施例的轴向截面图。Fig. 3 is an axial sectional view of a second embodiment of the present invention.

图4是叶片的透视图，表示了图3所示实施例中流动状态。FIG. 4 is a perspective view of a vane showing flow conditions in the embodiment shown in FIG. 3 .

图5是本发明的第三实施例的轴向截面图。Fig. 5 is an axial sectional view of a third embodiment of the present invention.

图6是本发明的第四实施例的轴向截面图。Fig. 6 is an axial sectional view of a fourth embodiment of the present invention.

图7是本发明的第五实施例的轴向截面图，它是沿着包含叶轮的转动轴线的平面截取的。Fig. 7 is an axial sectional view of a fifth embodiment of the present invention, taken along a plane containing the axis of rotation of the impeller.

图8是图7所示实施例的固定叶片的平面图，表示了叶片的设置情况。Fig. 8 is a plan view of the fixed vane of the embodiment shown in Fig. 7, showing the arrangement of the vanes.

图9是图7所示实施例的固定叶片的透视图，表示了叶片的设置情况。Fig. 9 is a perspective view of the fixed blade of the embodiment shown in Fig. 7, showing the arrangement of the blade.

图10是本发明的第六实施例的轴向截面图。Fig. 10 is an axial sectional view of a sixth embodiment of the present invention.

图11是本发明的第七实施例的轴向截面图。Fig. 11 is an axial sectional view of a seventh embodiment of the present invention.

图12是图11所示实施例中固定叶片的透视图。FIG. 12 is a perspective view of the stationary vane in the embodiment shown in FIG. 11. FIG.

图13是本发明第八实施例的透视图。Fig. 13 is a perspective view of an eighth embodiment of the present invention.

下面结合附图描述本发明的优选实施例。Preferred embodiments of the present invention are described below in conjunction with the accompanying drawings.

先参见图1和2，它们示出了本发明的第一实施例。由叶轮1压缩的流体流2被引入到一扩压器中，此扩压器由侧壁9和主侧壁10构成。在扩压器中设置有固定叶片4，以把流体流2的动能高效地转换成压力。从扩压器流出的流体流2经蜗壳3导入与压缩机排出侧相连的管道(未示出)。为了将流体流2的动能高效地转换成压力，必须使位于固定叶片4之间的流道在扩压器出口侧的截面有较大的数值。因此，每个固定叶片4位于出口侧的边缘与径向所成的叶片角β2设计成大于该叶片4位于进口侧的边缘与径向所成的叶片角β1。另一方面，希望使出口侧的固定叶片角度β2大于进口侧的叶片角度β1，因为进入蜗壳3的流体流的径向速度分量所具有的绝大部分动能会通过与蜗壳3中的流体流冲撞而损失掉。由于每个固定叶片4的出口侧高度h2大于其进口侧高度h1，所以很容易为在出口侧的固定叶片4之间的流道提供必要的流道截面。因此，与h2等于等于h1的情况相比，此时能减小外径d2，从而使离心式压缩机的总体尺寸减小。另外，由于可将压缩机设计成让出口侧的叶片角度β2大于进口侧的叶片角度β1，所以可减小出口侧的径向速度分量，这样就降低了来自扩压器的流体流在蜗壳3中的损失。利用这种效应，就能提高离心式压缩机的效率。Referring first to Figures 1 and 2, there is shown a first embodiment of the present invention. The fluid flow 2 compressed by the impeller 1 is introduced into a diffuser formed by a side wall 9 and a main side wall 10 . Stationary vanes 4 are provided in the diffuser to efficiently convert the kinetic energy of the fluid flow 2 into pressure. The fluid flow 2 from the diffuser is directed via the volute 3 into a duct (not shown) connected to the discharge side of the compressor. In order to efficiently convert the kinetic energy of the fluid flow 2 into pressure, the flow channel between the stationary vanes 4 must have a large cross-section on the diffuser outlet side. Therefore, the vane angle β 2 formed by the edge of each fixed vane 4 on the outlet side and the radial direction is designed to be larger than the vane angle β 1 formed by the edge of the vane 4 on the inlet side and the radial direction. On the other hand, it is desirable to make the fixed vane angle β2 on the outlet side larger than the vane angle β1 on the inlet side, because most of the kinetic energy of the radial velocity component of the fluid flow entering the volute 3 will pass through the Fluid streams collide and are lost. Since the outlet-side height h 2 of each stationary vane 4 is greater than its inlet-side height h 1 , it is easy to provide the necessary flow channel section for the flow channel between the stationary vanes 4 on the outlet side. Therefore, compared with the case where h 2 is equal to h 1 , the outer diameter d 2 can be reduced at this time, thereby reducing the overall size of the centrifugal compressor. In addition, since the compressor can be designed so that the vane angle β 2 on the outlet side is greater than the vane angle β 1 on the inlet side, the radial velocity component on the outlet side can be reduced, which reduces the fluid flow from the diffuser at Loss in volute 3. Utilizing this effect, the efficiency of the centrifugal compressor can be increased.

在常规结构中，如果每个固定叶片4的出口侧高度h2与进口侧高度h1相互不同的话，侧壁9和主侧壁10中的一个或两者都被加工成具有例如象锥面这样的曲面。在这种情况下，难于对固定叶片4的材料进行加工。也就是说，如果要通过切削一块坯料而整体加工出固定叶片4以及支承它们的侧壁9或主侧壁10的话，则很难利用车床将位于固定叶片4之间的侧壁9或主侧壁10的各个部分加工成一个曲面(如一个锥面)。在这种情况下，粗加工之后需要利用端磨机进行长时间的精加工，由此增加了加工步骤。如果将每个固定叶片4和支承它的侧壁9或主侧壁10加工成彼此分立的构件，那么就需将固定叶片4进行固定并且增加了组成零件的数目。在本发明的这个实施例中，固定叶片4是与侧壁9或主侧壁10上的一个垂直于叶轮1的转动轴线方向的平表面整体成形的，因此，当将一块坯料切削形成固定叶片4和支承它的侧壁9或主侧壁10时，易于使用端磨机进行加工。In a conventional structure, if the outlet-side height h2 and the inlet-side height h1 of each stationary vane 4 are different from each other, one or both of the side wall 9 and the main side wall 10 are processed to have, for example, a conical surface such a surface. In this case, it is difficult to process the material of the stationary blade 4 . That is to say, if the stationary vanes 4 and the sidewalls 9 or main sidewalls 10 supporting them are integrally processed by cutting a piece of blank, it is difficult to make the sidewalls 9 or main sidewalls 9 between the stationary vanes 4 by a lathe. Each portion of the wall 10 is machined into a curved surface (eg, a tapered surface). In this case, long-time finishing with an end grinder is required after rough machining, thereby increasing the number of machining steps. If each stationary vane 4 and the side wall 9 or main side wall 10 supporting it are processed as separate members from each other, then the stationary vane 4 needs to be fixed and the number of constituent parts increases. In this embodiment of the present invention, the fixed blade 4 is integrally formed with a flat surface on the side wall 9 or the main side wall 10 that is perpendicular to the direction of the axis of rotation of the impeller 1. Therefore, when a piece of blank is cut to form the fixed blade 4 and the side wall 9 or main side wall 10 that supports it, it is easy to use an end mill for processing.

图3和图4示出了本发明的第二实施例。图3是固定叶片4的轴向截面图，而图4是其透视图。3 and 4 show a second embodiment of the invention. FIG. 3 is an axial sectional view of the stationary blade 4, and FIG. 4 is a perspective view thereof.

此实施例的特征在于，每个固定叶片4的靠近侧壁9的前缘部分5延伸到比叶片4的靠近主侧壁10的前缘部分6更接近叶轮1。This embodiment is characterized in that the leading edge portion 5 of each stationary blade 4 close to the side wall 9 extends closer to the impeller 1 than the leading edge portion 6 of the blade 4 close to the main side wall 10 .

下面参照图4说明这种结构的效果。在低流量运转期间，在叶轮1的出口，侧壁9附近的流体的静压力小于主侧壁10附近的流体的静压力，而且在接近于叶轮的切线方向8的方向上易于产生逆流，叶轮的切线方向8与速度矢量7的方向是不同的。为此，使每个固定叶片4的靠近侧壁9的前缘部分5更接近叶轮1，以强制引导来自叶轮1的流体流，以抑制在叶轮出口和固定叶片4的前缘之前出现逆流。其结果是，在扩压器中不易发生流体阻塞，确保压缩机在低流量下的运转范围变宽。The effect of this structure will be described below with reference to FIG. 4 . During low-flow operation, at the outlet of the impeller 1, the static pressure of the fluid near the side wall 9 is lower than that of the fluid near the main side wall 10, and reverse flow is easy to occur in the direction close to the tangential direction 8 of the impeller, and the impeller The tangent direction 8 of is different from the direction of the velocity vector 7 . To this end, the leading edge portion 5 of each stationary blade 4 near the side wall 9 is brought closer to the impeller 1 to forcibly guide the fluid flow from the impeller 1 to suppress reverse flow between the impeller outlet and the leading edge of the stationary blade 4 . As a result, flow blockage is less likely to occur in the diffuser, ensuring a wide operating range of the compressor at low flow rates.

图5是本发明第三实施例的轴向截面图。Fig. 5 is an axial sectional view of a third embodiment of the present invention.

在第三实施例中，每个固定叶片4的前缘是阶梯形的，以分别形成靠近侧壁9和主侧壁10的两个前缘部分，这两个前缘部分由一径向延伸的直线连接，由此简化了成形固定叶片前缘的加工作业。In the third embodiment, the leading edge of each stationary vane 4 is stepped to form two leading edge portions near the side wall 9 and the main side wall 10 respectively, which are defined by a radially extending The linear connection of the blades simplifies the processing work for forming the leading edge of the fixed blade.

图6是本发明的第四实施例的轴向截面图。Fig. 6 is an axial sectional view of a fourth embodiment of the present invention.

在第四实施例中，每个固定叶片4的前缘是阶梯形的，以形成分别靠近侧壁9和主侧壁10的两个前缘部分，这两个前缘部分由一斜线连接，由此简化了成形固定叶片前缘的加工作业。In the fourth embodiment, the leading edge of each stationary vane 4 is stepped to form two leading edge portions adjacent to the side wall 9 and the main side wall 10 respectively, and these two leading edge portions are connected by an oblique line , thereby simplifying the machining operations for forming the leading edge of the fixed blade.

图7、8和9示出了本发明的第五实施例。图7是离心式压缩机的轴向截面图，它是沿着包含叶轮转动轴线的平面截取的。图8是表示固定叶片设置情况的平面图。图9是表示固定叶片设置情况的透视图。7, 8 and 9 show a fifth embodiment of the invention. Fig. 7 is an axial sectional view of the centrifugal compressor, taken along a plane containing the axis of rotation of the impeller. Fig. 8 is a plan view showing the arrangement of stationary blades. Fig. 9 is a perspective view showing the arrangement of the stationary blades.

在此实施例中，在每个固定叶片4的进口侧附近设置有一个辅助叶片11。辅助叶片11的弦长小于固定叶片4的弦长，而其高度等于或小于固定叶片4的高度。辅助叶片11与侧壁9或主侧壁10上垂直于叶轮1转动轴线的平表面整体成形，使得辅助叶片11的两个表面中的一个表面对着一个相邻的固定叶片4。辅助叶片11具有分别靠近侧壁9和主侧壁10的两前缘部分，它们由一部分弯曲线连接。辅助叶片11上靠近侧壁9的前缘部分比其靠近主侧壁10的前缘部分更接近叶轮1。In this embodiment, one auxiliary vane 11 is provided near the inlet side of each stationary vane 4 . The chord length of the auxiliary blade 11 is smaller than the chord length of the fixed blade 4 , and its height is equal to or smaller than that of the fixed blade 4 . The auxiliary vane 11 is integrally formed with a flat surface on the side wall 9 or the main side wall 10 perpendicular to the axis of rotation of the impeller 1 such that one of the two surfaces of the auxiliary vane 11 faces an adjacent stationary vane 4 . The auxiliary blade 11 has two leading edge portions adjacent to the side wall 9 and the main side wall 10 respectively, which are connected by a part of a curved line. The leading edge portion of the auxiliary blade 11 close to the side wall 9 is closer to the impeller 1 than the leading edge portion thereof close to the main side wall 10 .

下面结合图8和9说明辅助叶片11的作用。The function of the auxiliary blade 11 will be described below with reference to FIGS. 8 and 9 .

辅助叶片11也具有强制引导来自叶轮1的流体的作用，以便抑制在叶轮1的出口和固定叶片4的前缘(如图4所示的固定叶片4上靠近侧壁9的前缘部分5)之间出现逆流、由于辅助叶片11独立于固定叶片4，所以那种通过增加固定叶片4数量所实现的效果，也能在扩压器的进口处实现，而且本实施例的引导作用高于上述第二实施例。如果仅简单地增加固定叶片4的数量而不改变其基本结构，则扩压器的性能会由于叶片间流道截面的减小和湿润而增大而降低。在本实施例中，辅助叶片11设置成仅使其两个表面中的一个面对相邻的固定叶片4，以避免叶片间流道截面减小。由于每个辅助叶片11在弦长上小于固定叶片4，而在高度上等于或小于固定叶片4，所以湿润面的增加量是很小的。因此与那种仅简单地增加固定叶片4的数量而不改变基本结构的情况相比，本实施例不会使扩压器性能明显下降。本实施例比第二实施例更能扩大压缩机在低流量侧的运转范围。Auxiliary vane 11 also has the effect of forcibly guiding the fluid from impeller 1, so as to restrain the outlet of impeller 1 and the leading edge of fixed blade 4 (as shown in Figure 4, the leading edge portion 5 of fixed blade 4 near side wall 9) There is a reverse flow between them, and since the auxiliary blades 11 are independent of the fixed blades 4, the effect achieved by increasing the number of fixed blades 4 can also be realized at the inlet of the diffuser, and the guiding effect of this embodiment is higher than that of the above-mentioned Second embodiment. If the number of fixed blades 4 is simply increased without changing its basic structure, the performance of the diffuser will be reduced due to the decrease in cross-section of the flow path between the blades and the increase in wetting. In this embodiment, the auxiliary vane 11 is arranged such that only one of its two surfaces faces the adjacent fixed vane 4 in order to avoid a reduction in cross-section of the flow path between the vanes. Since each auxiliary blade 11 is smaller than the fixed blade 4 in chord length and equal to or smaller than the fixed blade 4 in height, the increase of the wetted surface is very small. Therefore, compared with the situation where the number of fixed vanes 4 is simply increased without changing the basic structure, this embodiment will not significantly reduce the performance of the diffuser. This embodiment can expand the operating range of the compressor on the low flow side more than the second embodiment.

图10是本发明的第六实施例的轴向截面图。Fig. 10 is an axial sectional view of a sixth embodiment of the present invention.

在第六实施例中，每个辅助叶片11的前缘是由一条平行于转轴13的轴线的直线构成的，因此简化了加工成形叶片前缘的作业。In the sixth embodiment, the leading edge of each auxiliary blade 11 is formed by a straight line parallel to the axis of the rotating shaft 13, thereby simplifying the work of forming the leading edge of the blade.

图11和12示出了本发明的第七实施例。图11是一个轴向截面图，而图12是固定叶片4的透视图。11 and 12 show a seventh embodiment of the present invention. FIG. 11 is an axial sectional view, and FIG. 12 is a perspective view of the stationary vane 4 .

在第七实施例中，在辅助叶片11的下游端上成形有一隔板12，隔板12的宽度小于相连的辅助叶片11的宽度，并且它沿着固定叶片4延伸，由此抑制了来自辅助叶片11根部的涡流，从而减小了由这种涡流所消耗的流动能量。结果是进一步提高了压缩机的效率。In the seventh embodiment, a partition 12 is formed on the downstream end of the auxiliary blade 11, the width of the partition 12 is smaller than that of the connected auxiliary blade 11, and it extends along the fixed blade 4, thereby suppressing the The vortex at the root of the blade 11 reduces the flow energy consumed by this vortex. The result is a further increase in compressor efficiency.

图13是表示本发明第八实施例的透视图。Fig. 13 is a perspective view showing an eighth embodiment of the present invention.

在第八实施例中，具有更伸近叶轮1的前缘固定叶片4和不具有这种前缘的固定叶片4是混合配置的。此外，伴随有辅助叶片11的固定叶片4和不伴随有辅助叶片11的固定叶片4是混合配置的。In the eighth embodiment, the fixed blades 4 having leading edges extending closer to the impeller 1 and the fixed blades 4 not having such leading edges are mixedly arranged. In addition, the fixed blades 4 with the auxiliary blades 11 and the fixed blades 4 without the auxiliary blades 11 are arranged in a mixed manner.

为了有效地设置这些不同的固定叶片4，可采用下面的结构。In order to effectively arrange these various fixed blades 4, the following structure can be adopted.

如果在扩压器下游设置一涡壳集流器，则设置在圆周方向的一舌形部分的下游侧的所有固定叶片4中的50％或小于50％的固定叶片4，不具有更伸近叶轮1的前缘部分，并且不伴随有辅助叶片11；而其余的固定叶片4都具有更伸近叶轮1的前缘部分，并且伴随有辅助叶片11。那些没有更伸近叶轮1的前缘部分且不伴随有辅助叶片11而设置的固定叶片4，与其它的那些具有更伸近叶轮1的前缘部分并且伴随有辅助叶片11的固定叶片4相比，更易引发流体分离。因此，一个流体分离区固定在那些没有更伸近叶轮1的前缘部分且不伴随有辅助叶片11的固定叶片4处，由此抑制旋转分离。如果不在扩压器下游设置象一条返回通道那样的舌形部分，则50％或小于50％的那种没有更伸近叶轮1的前缘部分且不伴随有辅助叶片11的固定叶片将被依次设置，以得到同样的效果。If a volute collector is arranged downstream of the diffuser, 50% or less of all the fixed blades 4 arranged on the downstream side of a tongue-shaped portion in the circumferential direction have no The leading edge portion of the impeller 1 without auxiliary blades 11; Those fixed blades 4 that do not extend closer to the leading edge portion of the impeller 1 and are not accompanied by auxiliary blades 11 are arranged in contrast to the other fixed blades 4 that have a closer portion of the leading edge of the impeller 1 and are accompanied by auxiliary blades 11. than, more likely to cause fluid separation. Therefore, a fluid separation zone is fixed at those stationary blades 4 that do not extend closer to the leading edge portion of the impeller 1 and are not accompanied by auxiliary blades 11, thereby suppressing rotational separation. If no tongue-shaped portion like a return passage is provided downstream of the diffuser, 50% or less of the fixed vanes that do not extend closer to the leading edge portion of the impeller 1 and are not accompanied by auxiliary vanes 11 will be sequentially removed. setting to get the same effect.

根据这个实施例，可以抑制扩压器的旋转分离，而这种分离易发生在低流量运转期间。According to this embodiment, the rotational separation of the diffuser, which tends to occur during low-flow operation, can be suppressed.

根据本发明，可以获得这样一种离心式压缩机，它易于制造，能提供从低流量到高流量宽的运转范围，而且它的体积紧凑。According to the present invention, there can be obtained a centrifugal compressor which is easy to manufacture, provides a wide operating range from low flow to high flow, and is compact in size.

Claims (6)

1. centrifugal compressor, it comprises:
An impeller;
A kinetic energy that is used for fluid that described impeller is discharged is converted to the Diffuser of pressure, and it has a sidewall and a major side wall, and one of described sidewall and major side wall are perpendicular with the rotation axis of described impeller; With
Be arranged on the stator blade in the described Diffuser;
Wherein, the perpendicular wall of the rotation axis of that in described stator blade and described sidewall and the major side wall and described impeller becomes one, and makes each described stator blade constitute a free end at the one end along the end face of its short transverse;
It is characterized in that, between described sidewall and major side wall in the distance of the suction side of described Diffuser less than distance in described diffuser exit side, each described stator blade at the height of described suction side less than height at described outlet side, near the radially angulation of each described stator blade of described outlet side and described impeller greater than this stator blade of close described suction side and the radially angulation of described impeller.
2. according to the centrifugal compressor of claim 1, it is characterized in that the leading edge portion of a close described sidewall on each described stator blade is than another the more approaching described impeller of leading edge portion near described major side wall on this stator blade.
3. according to the centrifugal compressor of claim 1 or 2, it is characterized in that, the wall unitary moulding that the rotation axis of that in auxiliary blade and described sidewall and the major side wall and described impeller is perpendicular, the chord length of each described auxiliary blade is less than the chord length of each described stator blade, and it highly is equal to or less than the height of each described stator blade, described auxiliary blade is arranged to the described entrance point near described stator blade, makes a surface in two surfaces of each described auxiliary blade facing to a relevant stator blade.
4. according to the centrifugal compressor of claim 3, it is characterized in that each described auxiliary blade has a leading edge that tilts to described major side wall from described sidewall.
5. according to the centrifugal compressor of claim 3, it is characterized in that a dividing plate is linked the downstream of each described auxiliary blade, and extend that the height of described dividing plate is less than the height of described auxiliary blade along a relevant stator blade.
6. according to the centrifugal compressor of claim 4, it is characterized in that a dividing plate is linked the downstream of each described auxiliary blade, and extend that the height of described dividing plate is less than the height of described auxiliary blade along a relevant stator blade.
CN95102414A 1994-03-18 1995-03-03 centrifugal compressor Expired - Fee Related CN1069742C (en)

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US5529457A (en) 1996-06-25
JP3153409B2 (en) 2001-04-09
KR0136302B1 (en) 1998-07-01
JPH07259796A (en) 1995-10-09
CN1116280A (en) 1996-02-07

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